Braking apparatus



March 29, 1938. J. c. M CUNE BRAKING APPARATUS Filed Feb. 1, 1936 '3 Sheets-Sheet l INVENTOR JUBEF'H C- MGBUNE 9%. 4/ ATTORNEY March 29, 1938. J, c, MCCUNE F 2,112,423

BRAKING APPARATUS Filed Feb. 1, 1936 3 Sheets-Sheet 2 fig. 2

INVENTOR .JIIIEEF'H E. MCEL'NE Evy ATTORN EY March 29, 1938. .1.- c. M CUNE BRAKING APPARATUS Filed Feb. 1, 3 Sheets-Sheet z INVENTOR JOSEPH C. McCUNE.

ATTORNEY types of brakes.

Patented Mar. 29, 1938 BRAKING APPARATUS Joseph 0. McCune, Edgewood, Pa., assignor to The Westinghouse Air Brake (lompany Wilmerding, Pa., a corporation of Pennsylvania Application February 1, 1936, Serial No. 61,961

26 Claims.

This invention relates to brake equipments, and more particularly to brake equipments for high speed trains and traction Vehicles.

In the design of high speed trains and traction Vehicles intended for city and suburban use great care is taken to produce quiet operation. One means employed to accomplish this is the provision of rubber inserts in the wheels so as to mechanically insulate the wheel treads 1 from the wheel hubs, and thereby minimize the amount of noise which is transmitted to the body proper. Where such rubber inserts are used in the wheels the braking which may be. permitted on the wheel treads must be limited, be-

15 cause if the wheel treads become overheated the rubber insulation may be wholly destroyed.

In order to secure adequate braking during normal stops, other means than the commonly employed shoe-on-wheel-type of brakes must 20 be used. In this connection it has been found desirable to employ both magnetic track brakes and dynamic brakes, the latter utilizing the driving motors, as is well understood in the art.

While magnetic track brakes and dynamic brakes alone may be employed when making normal stops, shoe-on-wheel-brakes, preferably of the fluid pressure operated type, must be provided to insure stopping of the train. or vehicle upon failure of either or both of the electric In addition, since the effectiveness of the dynamic brakes diminishes at low speeds, it is desirable that the fluid pressure brakes be cut into action at or about the time the dynamic brakes diminish in effectiveness, so

35 as to insure stopping and holding of the train or vehicle at rest.

It is a principal object of the present invention to provide an improved brake equipment employing fluid pressure brakes, magnetic track brakes,

4,0 and, dynamic brakes, in which the magnetic track brakes and dynamic brakes alone are employed for making normal stops, with the fluid pressure brakes held suppressed until the effectiveness of the dynamic brakes diminishes below a prede- 45 termined value, at which time the fluid pressure brakes are applied.

While it is desirable that the fluid pressure brakes be suppressed when making normal stops, in order to prevent injury to the rubber inserts 50 in the wheels, it is also desirable that means be provided for applying the fluid pressure brakes as well as the magnetic track and dynamic brakes when making emergency stops. It is therefore accordingly a further important object of the 55 present invention to provide a brake equipment of the type referred to in the foregoing object, Whichin addition provides for application of all three of the aforementioned brakes when effecting an emergency application.

Safety considerations require that means be 5 provided for effecting an application of the brakes on a vehicle when the operator thereof becomes incapacitated to perform his regular duties. Such means is commonly referred to as deadman control. It is a further object of the present invention to provide an improved brake equipment of the type hereinbefore referred to which has incorporated therein deadman control features.

In the design of a brake equipment of the type hereinbefore referred to, experience has taught the desirability of incorporating in such an equipment a number of desirable structural and operative features, and it is a further object of the present invention to incorporate a number of such features in a brake equipment of the type herein disclosed. The specific features included will be hereinafter more fully referred to and described.

A more complete understanding of the invention will be obtained from the following description, which is taken in connection with theattached drawings, wherein,

Fig. 1' is a schematic and diagrammatic view of one embodiment of the invention adapted for a single vehicle. r Fig. 2 is a diagrammatic View of the control valve device shown in the lower right hand portion of Fig. 1. v

Fig. 3 is a fragmentary diagrammatic vlew'of the derail throwing brake valve device shown to the upper left of Fig. 1.

Fig. 4 shows in schematic and diagrammatic form .a modification of the fluid pressure brake system shown in Fig. 1.

Referring now briefly at first to the embodi- 40 ment shown in Fig. 1, the fluid pressure brake system may comprise. a brake cylinder ID, a double check valve device II, a control valve device 12, an emergency reservoir l3, a main reservoir M, a fluid pressure operated switch device IS, a foot valve device H, a hand valve device I8, and a derail throwing brake valve device IS.

The magnetic track brake system may comprise a track brake device 22 suspended above a track rail 23, a raising cylinder 24, and a magnet valve device 25.

The dynamic brake system comprises the vehicle driving motors having armatures 26 and field windings 27, which are adapted to have power supplied thereto by operation of a motor 557 controller 28 when driving the vehicle, and to be connected in a dynamic braking circuit by operation of a controller device 39 when operated as dynamic brakes.

The controller device 30 forms a part of a common control mechanism for controlling applications of all three types of brakes in response to actuation of a service foot pedal 3| or a fluid pressure operated device 32.

In order that the fluid pressure brakes may be suppressed when making normal applications of the brakes, a relay 33 is provided in electrical association with the dynamic brake system, as will be more fully hereinafter described.

Considering now more in detail the apparatus above referred to, while only one brake cylinder l0, one magnetic track brake device 22, and a limited number of vehicle driving motors are shown, it will be apparent that any number of these devices may be employed as dictated by conditions.

Considering now in detail the control valve device l2, this valve device comprises a self-lapping valve section 35, a suppression magnet valve section 36 and an emergency valve section 31, all of which are secured to a pipe bracket section 38.

The self-lapping valve section is embodied in a casing defining a pressure chamber 39. This chamber is in communication with the brake cylinder ID by way of pipe and passage 49, double check valve device I I, and pipe 4|.

A supply valve 42, normally urged to seated position by a spring 43, is provided for'controlling the supply of fluid under pressure to the pressure chamber 39. A release valve 44, carried by a movable abutment 45 in the form of a piston, is provided for controlling the release of fluid under pressure from the chamber 39. The release valve 44 is urged toward unseated position by a spring 46. v The movable abutment 45 is subject on its lower side to pressure of fluid in chamber 39 and on its upper side to pressure of a regulating spring 41. Tension on this spring may be regulated by a regulating member 48, while upward movement of the movable abutment 45 may be limited by a set screw 49. I

When the supply valve 42 is seated and the release valve 44 unseated, the pressure chamber 391s in communication with the atmosphere by way of passages 59, chamber 5|, and pipe and passage 52. When the release valve 44 is seated and the supply valve 42 is unseated, fluid under pressure is supplied to the chamber 39 from the main. reservoir I4, by way of pipe and passage 53, the suppression magnet valve section 36, and passage 54.

For seating the release valve 44 and unseating the supply valve 42, there is provided a mechanism comprising a lever 56 pivotally carried intermediate its ends at 5'! by a plunger 58. At its left end the lever 56 carries a stem 59 which projects into a recess in the supply valve 42. At its right hand end the lever 56 carries a roller 60 which engages the stem of the release valve 44.

The plunger 58 is slidably disposed in a bore GI and may be actuated upwardly by an arm 62 secured to a shaft 63. When the plunger 58 is actuated upwardly the lever 56 first fulcrums about its left end to seat the release valve 44, against opposition of spring 46, and then fulcrums about its right end to unseat the supply valve 42, against opposition of its Spring 43. It 1 to be here understood that the release valve spring 46 is lighter than the supply valve spring 43, so that this operation may take place. During this operation the regulating spring 41 is unappreciably compressed, because it is considerably heavier than either the release valve spring 46 or the supply valve spring 43.

With the release valve 44 seated and the supply valve 42 unseated fluid under pressure will be supplied to the chamber 39, and as this pressure increases the movable abutment 45 will be actuated upwardly. As the movable abutment moves upwardly the lever 56 will fulcrum about its pivot 51 and rotate in a counterclockwise direction under action of the supply valve spring 43 until the supply valve 42 is seated, at which time the supply of fluid under pressure to the chamber 39 will be lapped. The parts are so designed that the pressure at which the lap operation takes place corresponds to the degree of upward movement of the plunger 58.

The upward movement of the plunger 58 is effected by rotation of a lever 65 also secured to the shaft 63. This lever 65 is biased to a release position by a spring 66, and may be actuated to various application positions by pull exerted on a connected link 61, as will hereinafter be more fully described. It will thus be apparent that the degree of rotation of the lever 65 in a counterclockwise direction determines the degree of upward movement of the plunger 58, and hence the degree of pressure in the pressure chamber 39. Since the chamber 39 is in communication with the brake cylinder l0, it follows that the degree of application of the fluid pressure brakes corresponds to the degree of counterclockwise rotation of the lever 65.

Also secured to the shaft 63 is a short arm 68 having pivotally secured thereto a finger 69 projecting into a slot 10 in the casing. When the shaft 63 is rotated in a counterclockwise direction, theflnger 69 drops into a recess H of a latch member 12.

The latch member 12 is secured to a shaft 13 which at its low-er end abuts against a piston 14. The piston 14 is disposed in a chamber 15 which is, normally charged with fluid under pressure, so that they piston 14 is positioned as shown in Fig. 2 to maintain the latch member 12 in the position illustrated.

The upper end of the shaft 13 is slidable in a guide member 16, and a spring 11 reacts between this guide member and the latch member 12 to urge the latch member downwardly. As long as the pressure of fluid supplied to chamber 15 is above a predetermined value the spring 11 will be overcome, but when the pressure is diminished below this predetermined value the spring 11 will actuate the latch member 12 downwardly, unless in the meanwhile the finger 69 has engaged the recess H to prevent the downward movement.

If, however, this has not taken place the latch member 12 will engage an arm '19 to rotate the shaft 63 through its full counterclockwise movement, to thus effect a supply of fluid under pressure to the pressure chamber 39 to a maximum degree. When fluid under pressure is again supplied to chamber 15 above the aforementioned predetermined degree the piston 14 will return to the position shown and spring 66 will then return lever 65 to its release position as illustrated.

The suppression magnet valve section 36 is embodied in a casing having a valve 80 urged toward an unseated position by a spring 8| and toward a seated position by an electromagnet (not shown) in the upper part of the valve device casing, which when energized actuates the valve downwardly to seated position.

The emergency valve section 31 is also embodied in a casing and is provided with a double beat valve 82 urged toward lower seated positionby a spring 83. A piston 84 disposed in a chamber 85 is adapted upon supply of fluid under pressure to this chamber to actuate the double beat valve 82 to upper seated position. The piston 84 is provided with a hollow stem 86 in which is disposed a spring 81 engaging a plunger 88 in contact with the stem of the double beat valve 82.

When the double beat valve 82 is in the lower seated position, as illustrated, a communication is established between the emergency reservoir I3 and the main reservoir I4, byway of pipe and passage 53, passage 90, past the open upper seat of the double beat valve 82, and pipe and passage 9|. When the double beat valve 82 is in its upper seated position this communication is closed and the emergency reservoir I3 is connected to the fluid pressure operated device 32, past the open lower seat of double beat valve 82, chamber 92, and pipe and passage 93.

The double beat valve 82 is actuated to upper seated position when fluid under pressure is supplied to the chamber 85 upon downward movement of the piston 14 in the self-lapping valve section 35. When the piston I4 is in its upper position, as illustrated, the chamber 85 is connected to the atmosphere-by way of passage: 89, chamber 94 and exhaust port 95. When the piston M moves to its lower position this communication to the atmosphere is cut off and passage 89 is opened to chamber 39, so that fluid under pressure flows from this chamber to the piston chamber 85. I

In the pipe bracket section I2 is provided a cut-off valve 98 urged toward a seated position by a spring 99. Chamber I below the valve 98 is in open communication with the main reservoir I4, and spring 99 above the valve is so designed that as long as main reservoir pressure is above a predetermined value the valve 98 will be held unseated, but when the pressure falls below this chosen value spring 99 will seat the valve 98. The valve 98 controls communication between the chamber I00 and a main reservoir pipe I DI and its branch pipe I02, which communication includes a ball check valve I03 and a passage I04. As will be observed, the ball check valve I03 permitsflow of fluid to the main reservoir pipe IOI but prevents flow in the op posite direction.

The double check valve device II is embodied in a casing comprising a slide valve I05 subject at its left end to pressure of fluid from a chamber I06 and at its right end to pressure of fluid from a chamber I 01. The slide valve I05 will move to the left or right depending upon whether the pressure in chamber I 06 or ID! is the greater.

The fluid pressure operated switch device I5 is embodied in a casing having a chamber I09 in which is disposed a piston I I0 urged downwardly by a spring I II. When the piston H0 is in its uppermost position a set of contacts II2 are maintained closed, and when the piston H0 is actuated to its lowermost position these contacts are opened.

The sanding valve device I5 is embodied in a casing provided with a valve II3 which is urged toward seated position by a spring II 4. The valve [I3 is provided with a stem II5 to which pressure may be applied to unseat the valve: and

thereby establish communication between the main reservoir branch pipe I02 and a sanding pipe I IE to cause sand to be applied to the track rails.

The foot valve device I1 is embodied in a casing provided with a supply valve II'I urged toward a seated position by spring H8, and alsowith a diaphragm valve I I9 coacting with a seat I20. A foot pedal I22 is provided for actuating these two valves. The foot pedal is pivotally mounted to the valve device casing at I23 and is normally urged upwardly by a spring I24. A pin I25 projecting into an aperture limits the up and down movement of the foot pedal When the foot pedal I22 is in the upper position, as illustrated, spring IIB holds valve II'I seated and diaphragm valve II9 away from its seat I20. This establishes communication between two sections of a safety control pipe I26. When the foot pedal I22 is manually actuated downwardly the diaphragm valve I I9 is caused to seat and the supply valve I I1 is unseated. This cuts off communication between the two sections of the safety control pipe I26, and establishes communication between the main reservoir pipe IOI and the lower section of the safety control pipe I26, through branch pipes I21 and I28.

It is to be here noted that the safety control pipe I26 is connected to the aforementioned chamber in the control valve device I2 by way of passage I29, and is also connected to the fluid pressure operated switch device I5 by way of branch pipe I30. While the pipe I26 has been specifically referred to as a safety control pipe, it is to be understood that this pipe is similar in function to other normally charged pipes referred to as brake pipe, emergency pipe, or the like.

The hand valve device I8 is embodied in a casing and has parts similar to the foot valve device I'I. A supply valve I32 controls communication between the main reservoir branch pipe I28 and the upper section of the safety control pipe I26. This valve is normally urged toward a seated position by spring I33 and is actuated to unseated position by downward movement of a handle I34. When the handle I34 is moved downwardly it effects seating of a diaphragm valve I35 to close communication between the upper section of the safety control pipe I26 and an exhaust port I 36.

Like the foot pedal in the foot valve device H, the handle I34 is pivo-tally mounted at I 31 and is urged upwardly by a spring I38. The up and down movement is limited by a pin I39 projecting into an aperture in the handle.

The derail throwing brake valve device I9 is embodied in a casing and is provided with a rotary valve I40 for controlling communication between the main reservoir pipe IOI and an application pipe I4I, and between the application pipe MI and an exhaust port I3I. A handle I42 is provided for rotating the rotary valve I40. When the handle I42 is in release position the pipe MI is connected to exhaust port I3I, as shown in Fig. 1. When the handle I42 is moved to application position the pipe MI is disconnected from the exhaust port I3I and connected to the main reservoir pipe IOI, as illustrated in Fig. 3.

A one-way check valve device I43 is disposed in the main reservoir pipe IIII adjacent the derail throwing brake valve device to permit the flow of fluid toward the brake valve device. but

to prevent flow in the opposite direction. This check valve deviceis of the spring loaded type, the spring being designed to limit the pressure of fluid supplied to the derail throwing brake valve device I9 to some value considerably below main reservoir pressure.

The magnetic track brake device 22 may be of any of the types commonly employed for pr ducing track braking. In the embodiment illustrated thetrack brake device is held suspended above a track rail 23 by a raising cylinder 24, which comprises a piston I 45 disposed in a chamber I46, and having astem attached to a bracket I41 secured to the track brake device 22. When fluid under pressure is supplied to the chamber I46 the piston I45 is actuated upwardly to hold the track brake device suspended above the track rail. When fluid under pressure is released from the chamber I46 the track brake device drops to the rail due to gravity effect.

The magnet valve device 25 controls the supply of fluid under pressure to and its release from the chamber I46. This magnet valve device comprises a double beat valve I48 urged toward an upper seated position by a spring I49, and to a lower seated position by action of an electromagnet in the upper part of the valve device casing which when energized actuates the double beat valve I48 downwardly.

When the double beat valve I48 is in its upper seated position fluid under pressure is supplied from the main reservoir pipe IIJI to the chamber I46 by way of pipe I58, past the lower seat of double beat valve I48, and pipe II. When the double beat valve I48 is in lower seated position this communication is cut off and the chamber I46 is vented to the atmosphere by way of exhaust port I52.

The controller device 30 preferably comprises a drum I54 secured to a shaft I55 and having disposed thereon and insulated therefrom separate contact segments I56, I51 and I58. The segment I56 is adapted to engage contact fingers I59 and I68; the segment I51 is adapted to engage contact fingers I6I to I64 inclusive; and the segment I58 is adapted to engage fingers I65 to I69 inclusive.

When the drum I54 is in release position, as illustrated, segment I56 is in engagement with contact fingers I59 and I68 so that the vehicle driving motors may be connected to a trolley I18. Power may then be supplied to the vehicle driving motors from the trolley I18 by way of conductor I'II, contacts I56, I59 and ISO, conductor I12, motor controller 28, and conductor I13, the return circuit to the source of power supply being by way of ground connection I14.

When the drum I54 is rotated through a predetermined movement segment I56 disengages from fingers I59 and I68 while at the same time segment I51 engages fingers I6! and I62 and one or both of fingers I63 and I64, depending upon the degree of rotation, while segment I 58 engages the three fingers I65, I65 and I51, and one or both of fingers I88 and I69 if the drum. is rotated far enough. The purpose of this arrangement will appear more fully from the: description of operation which follows hereinafter.

The shaft I55 has disposed thereon a cam I16 which engages one end of a lever I11 pivotally mounted at I18 and having its other end secured to link' 61 connected to the aforedescribed lever 65 associated with the control valve device I2.

The cam I116 is so designed that as the shaft I55 rotates in a counterclockwise direction the lever I11 is rotated in a clockwise direction to actuate the control valve lever 65 progressively to the left.

The fluid pressure operated device 32 is embodied in a casing and provided with a piston I80 subject on one side to pressure of fluid supplied to a chamber I8I and subject on the other side to pressure from a spring I82 acting through a rod I83.

One end of the rod I83 bears against the piston I88, while the other end engages a roller I connected to an arm I84 rigidly secured to. the shaft I55. The shaft I 55 also has rigidly disposed thereon a sheave or pulley I85 over which passes a cable I86. One end of the cable is fastened to a spring I81 the other end of which is secured to a bracket I88. In the arrangement of the parts illustrated in Fig. 1 the spring I81 is under tension so that the shaft I55 is positioned as shown.

When, however, an upward pull is exerted on the cable I86, or fluid under pressure is supplied to the chamber I8I of the fluid pressure operated device 32, the shaft I55 is rotated in a counterclockwise direction. Upward pull on the cable I86 may be effected by actuation of the foot pedal 36 downwardly. This foot pedal is pivotally mounted at I89 to some portion of the car body and has an extension arm I98 connected to one end of cable I86, the cable passing over an idler pulley ISI for the purpose of changing the direction of the applied force due to depressing the foot pedal 3 I. It should be obvious from the arrangement shown that the degree to which the shaft I55 is rotated by depressing the foot pedal 3I depends upon the degree to which the foot pedal is depressed.

Now when fluid under pressure is supplied to the chamber I8I of the fluid pressure operated device 32 to a degree such that the opposing force exerted by the spring I82 therein is wholly overcome, the shaft I55 is rotated to its extreme counterclockwise position, which corresponds to the emergency positionof the controller device 38, while the cam I18 actuates the control valve device I2 to emergency position, as will more fully hereinafter appear.

Fluid under pressure supplied to the chamber I8I flows to the atmosphere through a passage I82 which contains a choke I93. The choke I 93 is designed to gradually vent the chamber I8I to the atmosphere, so that when the fluid pressure operated device 32 actuates the shaft I55 to its emergency position it will maintain it there for a predetermined length of time and then permit spring I81 to return it to release position.

The operation of this embodiment of my invention is as follows:

Running condition When the vehicle is being driven under power, or coasting, the parts of the brake equipment illustrated are maintained in the positions shown in Fig. 1. It is to be not-ed that the handle I34 of the hand valve device I8 is held depressed while the foot pedal I22 is permitted to assume its uppermost position. It is to be here understood that while the vehicle is being driven under power, or coasting, that either the handle I34 or the foot pedal I22 must be held depressed by the operator.

With the controller device 30 in the position shown contact segment I56 will connect fingers I59 and I60, so that power may be supplied to the ,vehicle driving motors through operation of the motor controller 28.

With either or both the handle I34 and the foot pedal I22 held depressed, the safety control pipe I26 will be charged to main reservoir pressure from the main reservoir pipe IOI. With the safety control pipe thus charged, piston 14 in the control valve device I2 will be held in its uppermost position, as illustrated in Fig. 2, and contacts I I2 of the fluid pressure operated switch device I5 will be maintained closed, as illustrated in Fig. 1.

It will be noted that the emergency reservoir 13 will, for the release positions of the parts shown, he charged from the'main reservoir I4 by v way of the communication leading past the open upper seat of the double beat valve 82 in the emergency valve section 31.

Service application When it is desired to effect a service application of the brakes, the operator depresses the service foot pedal 3I to a degree according to the desired degree of braking, while at the same time maintaining pressure manually applied to either the handle I34 or the foot pedal I22. Depressing the service foot pedal 3| rotates the shaft I55 correspondingly. As the shaft thus rotates the cam I16 causes actuation of lever 65 in a counterclockwise direction, whereupon release valve 44 (in the control valve device I2) will be seated and the supply valve 42 will be unseated. Therefore, were it not for an operation to be subsequently described fluid under pressure would be supplied fromv the main reservoir I4 to the chamber 39, and from thence would flow to the brake cylinder I0.

The fiow from the main reservoir would be by way of pipe and passage 53, past the unseated valve 80 in the magnet valve portion 36, passage 54, and past the ,unseated supply valve 42; The

flow from chamber 39 to the brake cylinder I would be by way of pipe and passage 40, double check valve device I I, in which the slide valve I will be actuated to the left, and pipe 4|.

Assuming now that the shaft I55 has been rotated far enough for contact segment I56 tobe disengaged from contact fingers I59 and I60, and for contact segment I51 toengage at least contact fingers I6I and I62, it will be apparent that the vehicle driving motors will be disconnected from the trolley I and will then be connected in a dynamic braking circuit, whichincludes conductors I95, contacts I51, I6I and I62, resistance I96, conductor I91, resistance I98, and conductor I99. The vehicle driving motors will thus be operated as dynamic brakes. It will further be apparent that if the contact segment I51 engages either or both of fingers I63 and I64 that the amount of the resistance I96 in the circuit will be reduced, or wholly cut out, so that the degree of dynamic braking will be increased.

As current fiows in the dynamic braking circuit through the resistor I98, the relay 33 will be energized and will close its contacts 200. Closing of these contacts energizes the suppression magnet valve section 36 of the control valve device I2, from a battery 205 through a circuit which includes conductor 20!, contacts 200, conductor 202, contacts H2 of the switch device I5, conductor 203, the magnet valve section 36, and ground connection 204.

The magnet valve section 36 Will immediately be energized to seat its valve 80. Seating of this valve closes the communication between the main reservoir I4 and the seat of the supply valve-42 in the self-lapping valve section 35. Thus fluid under pressure is prevented from being supplied to the brake cylinder I0 so long as relay 33 is energized.

At the time the vehicle motors were connected in a dynamic braking circuit, contact finger I58 engaged, the three contact fingers I65, -I66fand I61. Engagement with fingers I65 and I66 establishes a circuit to the magnet valve device 25, from the battery 205, through a circuit which includes conductor 206, contact fingers I65 and I66, conductor 201, magnet valve device 25, and ground connection 208. Magnet valve device 25 will then actuate its double beat valve I48 to lower seated position, to vent the chamber I46 in the raising cylinder 24. The track brake device 22 will then drop by gravity to engagement with the track rail.

At the same time, engagement of segment I58 with fingers I65 and 161 establishes a circuit from the battery 205 to the track brake device 22, which beginning at finger I65 includes finger I61, resistance 209, conductor 2 I0, the track brake device 22, and ground connection H I. .If the segment I58 engages: one or both of fingers I68 and I69 the resistance 209 will be partially or wholly cut out, so as to increase the degree of energization of the winding in the track brake device 22.

It will thus be obvious from the foregoing description that when the shaft I55 is rotated to a degree sufficient to apply both the dynamic and track brakes that the fluid pressure brakes will be suppressed, and will be applied only when the dynamic braking decreases sufficiently for relay 33 to open contacts 200, as near the end of. the stop. 1

It should be further apparent that the degree of braking maybe varied by varying the degree to which the service foot pedal 3I is depressed. If the foot pedal 3I is depressed to its limit the dynamic and track brakes will be applied to their maximum degree, while at the same time a finger 2I2 attached to the sheave or pulley I85 engages the stem H5 in the sanding valve device I6 and unseats the valve II3. Unseating of this valve supplies fiuid under pressure from the main'reservoir pipe I02 to the sanding pipe I I6 to effect a deposit of sand on the rail. This increases the adhesion between the wheels and rails so as to prevent, or at least minimize the danger of, wheel sliding.

When it is desired to effect a release of the brakes, the foot pedal 3| is permitted to return to its release position, which is that shown in Fig. 1, whereupon spring I81 will return the shaft I55 to its release position. Both the dynamic and track brakes will'then be released and the parts will assume the positions shown in Fig. 1.

The track brake device 22 has been shown as held. suspended in its inoperative or release position above the rail by a raising cylinder, and lowered to the rail by venting the cylinder. It is to be understood, however, that the invention is not limited to this particular arrangement, but that the track brake device may be held suspended above the rail on springs and attracted to the rail upon energization thereof. Or as another alternative, the track brake device may be held suspended above the rail by springs and actuated toward or into engagement with the rail by electromagnets or similar devices. All of these methods of suspension and actuation of the track brake device into engagement with the rail are Emergency application When it is desired to effect an emergency application of the brakes, pressure manually applied to one or both of the handle I34 and foot, pedal I22 is released, to permit both of these elements to be actuated by their associated springs to their uppermost position.

In the hand valve device I8, the upward move ment of the handle I34 effects seating of the valve l32, to close" Communication between the main reservoir branch pipe I28 and the upper portion of the safety control pipe I26, while the diaphragm valve I35 moves away from itsseat to establish a communication between the safety control pipe I26'and exhaust port I36.

In the foot valvedevice II, the upward movement of the foot pedal I22 effects seating of the supply valve In andunseating of the diaphragm valve I I9. Unseating of the supply valve II'I cuts off communication between the main reservoir branch pipe I 28 and the lower portion of the safety control pipe I26, while unseating of the diaphragm valve I I9 connects the two portions of the safety control pipe I26, so that the whole safety control pipe is vented to the atmosphere by way of the exhaust port I36 in the hand valve device I8.

As the pressure of fluid in the safety control pipe diminishes due to this venting, the piston I4 in the control valve device I2 will move downwardly under action of spring II. The latch member 12 will then engage the lower end of the arm I9 and actuate the plunger '58 to its extreme uppermost position. This will position the parts to'supply fluid under pressure to the pressure chamber 39 toa maximum degree.

At the same time, as piston 74 moves downwardly itcloses the communication from the piston chamber 85 in the emergency valve section 31 to the atmosphere, and connects the piston chamber 85 to the pressure chamber 39.

Since now the communication from the main reservoir I4 to the seat of supply valve 42 is open, fluid under pressure flows to chamber 39, and from thence to both the brake cylinder III and to the piston chamber 85. The pressure of fluid in the piston chamber 85 actuates piston 84 upwardly, and shifts double beat valve 32 to its upper seated position. This establishes a communication between'the emergency reservoir I3 and pipe and passage 93 leading to the fluid pressure operated device 32. f Fluid under pressure then flows from emergency reservoir I3 through pipe and passage 9|, past the open lower seat of double beat valve 82, through chamber 92, pipe and passage 93, to chamber I8I in the fluid pressure operated device -32.

Piston I89 in this device is then actuated downwardly, and rod I83 engages the roller I15 carried by the arm 584 to actuate shaft I55 to its extreme clockwise or emergency position. The controller device 30 is then actuated toemergency I position to effect an application of both the dynamic and magnetic track brakes to a maximum degree, as heretofore described.

' When the safety control pipe I26 was vented to the atmosphere the pressure in chamber I09 of the switch device I was correspondingly reduced so that contacts IIZ are opened. Opening of these contacts prevents energization of the suppression magnet valve section 36 upon application of the dynamic brakes.

Thus. during an; emergency application the fluid pressure brakes, the dynamic brakes, and the magnetic track brakes are all applied to a maximum degree.

Since the chamber I8I in. the fluid pressure operated device 32 is in restricted communication with the atmosphere by way of choke I93, it will be obvious that after 'a predetermined length of time, which is made long enough to insure'that the vehicle will be stopped, the pressure in the emergency reservoir I3 and chamber I8I will diminish to a value such that spring I82 will return the piston I 80. to the position shown in Fig. 1, and thereby effecta release of the dynamic and magnetic track'brakes.

To recharge the safety control pipe I26 pressure is again manually applied to the handle I34 or the foot pedal I22, whereupon the parts of the control valve device I2 will assume the position shown in Fig. 2, to release the fluid pressure brakes.

Deraz'l throwing application When the vehicle approaches an open derail switch and it is desired to close the switch so that the vehicle may pass, the vehicle is brought to a stop by efiecting an application through operation of the derail throwing brake valve device I9. The handle I42 of this device is'turned to application position to establish the communication shown in Fig.3. The main reservoir pipe IOI is thus connected to the application pipe IM to supply fluid under pressure to the brake cylinder III, the slide valve I95 in the double check valve device I I being shifted to its right hand position.

At the same time, the foot pedal 3| is permitted to remain in its release position, so that the controller device 30Ido'es not isolate the vehicle driving motors from the trolley I10. The operator then operates the motor controller 28 to supply power to the vehicle driving motors. The current which flows from' the trolley and through ground connection I14 to the track rails flows through an'electromagnet in the derail switch, and the action of this electromagnet closes, the derail switch.

The operator then eifects a release of the fluid pressure brakes by turning the derail throwing brake valve handle I42 back to release position. The vehicle may then pass the derail switch.

It will thus be seen that when effecting a derail throwing application the fluid pressure brakes only are applied by operation of an auxiliary application means. It is to be noted that if at any time the main reservoir pipe IOI should become ruptured, cut-off valve 98 will seat to prevent loss of pressure below a chosen value, as hereinbefore described.

Modification shown in Fig. 4

This modification deals with the fluid pressure brake portion only of the equipment shown in Fig. l, and illustrates an arrangement for providing functions not present in the equipment illustrated in Fig. 1. It is to be understood, however, that the modified fluid pressure brake system shown in Fig. 4 is intended to operate in conjunction with the dynamic brake and magnetic track brake systems illustrated in Fig. l, in substantially the manner described in connection with that figure.

In the system illustrated in Fig. 4, the emergency reservoir I3, main reservoir I4, brake cylinder I0, foot valve device I1, and fluid pressure operated device 32 of Fig. 1 are retained. The

control valve device I 2 of Fig. 1 is rep-laced by the control valve device 2|5, while a conductors valve device 2|6 has been added to the system. The other fluid pressure brake devices illustrated in Fig. 1 and not shown in Fig. 4 have been or may be omitted, or incorporated in the new control valve device 2 |5.

The control valve device 2|5 comprises a selflapping valve portion 2 I8, a suppression magnet valve portion 2|9, an emergency valve portion 228, and a pipe bracket portion 22|, which sections are similar to the corresponding sections of the control valve device l2.

The parts of the self-lapping valve section 2 l8 which correspond to the self-lapping valve section 35 of Figs. 1 and 2 are similarly numbered in Fig. 4. In Fig. 4 a cam 223 secured to the shaft 63 has replaced the arm 62 of Fig. 2. This cam 223 is designed to actuate the plunger 58 upwardly in the same manner as the arm 62.

The piston 14 of Fig. 2, and the mechanism associated therewith, have been omitted and replaced in Fig. 4 by a holding mechanism comprising a piston 224 disposed in a chamber 225 and urged toward the left by a spring 226. The piston 225 has associated therewith a stem 22'! which is adapted to rock a bell crank lever 228,

1 one arm of which comprises a cam 229 adapted to engage a collar 238 secured to the shaft 63.

When fluid under pressure to a predetermined degree is supplied to and maintained in the chamher 225 the piston 224 is positioned as shown in Fig. 4 in which case the cam 229 is maintained out of engagement with the collar 230. When fluid under pressure in-chamber 225 is released or diminished, spring 226 actuates piston 224 to the left and thereby causes cam 229 to engage the collar 230. If in the meanwhile the shaft 63 has been rotated to a position corresponding to an application position the cam 229 will act as a wedge and hold the shaft 63 in this application position until fluid under pressure is again supplied to chamber 225 toa degree sufficient to disengage cam 229 from the collar 230.

The self-lapping section has also incorporated therein a sanding valve 232 which is urged toward seated position by a spring 233 and is adapted to be unseated by engagement of a finger 234, rotatable with the shaft 63, with valve stem 235. When unseated the valve 232 establishes communication between emergency reservoir I3 and a sanding pipe H6, referred to in the embodiment of Fig. 1, the communication being established by way of pipe and passage 9|, and passage 236. r

The suppression magnet valve section 2| 3 is similar in function to the suppression magnet valve section 36 of Fig. 1, except that in Fig. 4 a relay valve 238 has been included to increase the flow capacity through this section. It will also be noted that whereas in the embodiment of Fig. l, and as specifically illustrated in Fig. 2, the suppression magnet valve section is disposed between the main reservoir l4 and the self-lapping portion 25, the suppression magnet valve section 2| 9 of Fig. 4 is disposed between the selflapping section 2| 8 and the brake cylinder Ill.

The relay valve 238 controls communication between passage 48 leading to chamber 39 of the self-lapping section, and pipe and passage 239 leading to brake cylinder Ill. The valve 238 is urged toward a seated .position by a light spring 240, and may be unseated by the pressure of fluid therebelow when this pressure exceeds that existing in chamber 24| above! the valve.

to unseat the vent valve 251.

The pressure of fluid in the chamber MI is controlled by a supply valve 242 and a release valve 243. A spring 231 urges the supply valve 242 to seated position and the release valve 243 to unseated position, while an electromagnet in the upper part of the valve device casing operates when energized to seat the release valve 243 and unseat the supply valve 242. When the release valve is seated and the supply valve unseated, fluid under pressure may flow from'passage 40, through passage 244, past the unseated valve 242, and through passage 245 to chamber 24|. A ball check valve 246 prevents flow to the brake cylinder l0, but permits a release of fluid under pressure from the brake cylinder when relay valve 238 is seated. When the pressure in chamber 24| is substantially equal to that in passage 48, spring 240 will seat the valve 239.

When supply valve 242 is seated and release valve 243 is unseated, chamber MI is vented to the atmosphere, whereupon the pressure in passage 48 may unseat valve 238 and fluid under pressure thereby flow to the brake cylinder Ill.

The emergency valve section 225 in Fig. 4 is similar to that illustrated in Fig. 2, except that the double beat valve 62 has been replaced by two valves 248 and 249 having fluted stems arranged in abutting relationship, the valve 248 being urged to seated position and the valve 249 to unseated position by a spring 250.

The emergency valve section of Fig. 2 operated upon an increase of pressure in the chamber 85 whereas the emergency valve section of Fig. 4 operates upon a decrease of pressure in chamber 85. The valves 248 and 249 are therefore normally positioned as shown in Fig. 4 when fluid under pressure is supplied to and maintained in the piston chamber 85, and are operated to seated and unseated positions respectively upon decrease of' pressure in this chamber.

The piston'chamber 85 is in communication by way of the aforedescribed passage 89 with a charging pipe 252, and is also in communication with the aforedescribed passage 99 which leads by way of ball check valve 253 to chamber 254 above the valve 248. It will thus be seen that when the valve 248 is maintained unseated, the emergency reservoir I3 is charged from the charging pipe 252, byway of passages 89 and 90, past ball valve 253, chamber 254, past the unseated valve 248, and pipe and passage 9|.

The conductors valve device 2|6 is embodied in a casing provided with a charging valve256 and a vent valve 251. vent valve 25! toward seated position while at the same time urging the charging valve 256 to unseated position.

For seating the charging valve 256 and unseating the vent valve 251, there is provided a lever 252 which is pivotally rotatable about afulcrum 268 to actuate an arm 255i downwardly. Downward movement of the arm 26| engages stem 262 Unseating of this valve eilects seating of the charging valve 256 through a spring 253 which permits relative movement between the two valves. 1

When the release valve 251 is seated and the charging valve 256 is unseated a communication is established between the main reservoir pipe HM and the charging pipe 252, by way of branch pipe 254. When the charging valve 256 is seated and. the vent valve 251 unseated this communication is cut off and the charging pipe 252 is I A spring 258 urges the vented to the atmosphere through an exhaust port 265.

In the embodiment of Fig. l a safety control pipe was provided which connected to the foot valve device ii and to the control valve device I2 of that embodiment. In the embodiment of Fig. 4 the safety control pipe has been omitted and a locking pipe 296 is provided which connects to the foot valve device I1 and to the control valve device 2I5. In the control valve device 2 I 5 the locking pipe is in communicaton with the aforedescribed chamber 225, by way of passage 25?, and is also in communication with the passage 89 leading to the charging pipe 252, by way of ball check valve 258.

The operation of this modified form of my invention is as follows:

Operation of modification of Fig. 4

When the vehicle is running under power, or coasting, the operator maintains pressure manually applied to the foot pedal I 22 of the foot valve device I1. This maintains the diaphragm valve H9 seated and the supply valve II'I unseated. The locking pipe 269 is then maintained in communication with the main reservoir pipe IUI by way of choke 269, so that the locking pipe 269 is charged tomain reservoir pressure. The pressure in chamber 225 in the control valve device 2I5 then corresponds to locking pipe pressure.

At the same time, the main reservoir pipe I9! is maintained in communication with the charging pipe 252 through the conductors valve device 2I, in which the parts will be in the positions as shown for this condition. The pressure in piston chamber of the emergency valve portion 220 will then also correspond to main reservoir pressure, and the emergency reservoir I3 will be charged past the unseated valve 248 from the main reservoir I4.

A service application of the brakes is effected by depressing the service foot pedal 3I, in which case the dynamic brakes and magnetic track brakes will be applied and the fluid pressure brakes will be suppressed by energization of the suppression magnet valve section 2I9 in the control valve device 2 I5. As has been previously described, energization of the suppression magnet valve section will cause relay valve 238 to remain seated, so that operation of the self -lapping valve section 2I8 due to rotation of shaft I55 will not result in the supply of fluid under pressure to the brake cylinder I0.

The functioning of the modified form of brake equipment from this point on is substantially the same as that described in connection with the embodiment of Fig. 1.

When the vehicle has been brought to a stop, if for any reason the operator desires to leave his station or requires the use of his feet for other functions, he may release pressure manually applied to the foot pedal I22, in which case the locking pipe 269 will be disconnected from the main reservoir pipe [BI and be connected to an eX- haust port 210. The locking pipe 266 will be thus vented to the atmosphere, and the resulting decrease of pressure in chamber 225 in the control valve device will permit piston 224 to move to the left, and by engagement of cam 229 with collar 230 lock the self-lapping valve portion 2I8 in the application position to which it has been previously actuated by manipulation of service foot pedal 3|.

It is to be noted'that reducing the pressure in the locking pipe 266 does not result in reducing the pressure in the piston chamber 85 of the emergency valve portion because of the presence of the ball check valve 268 in the communication between the locking pipe and this piston chamber.

When pressure is again manually applied to the foot pedal I22 the holding function performed by the cam 229 will be terminated so that a release of the brakes may be effected by returning the service foot pedal 3| to its release position. I

In the embodiment of Fig. 1 an emergency application of the brakes was effected by simultaneously releasing pressure manually applied to the handle I34 and the foot pedal I22. In the embodiment of Fig. 4, an emergency application is effected by rotary movement of the lever 259 in the conductors valve device 2I6. As previously described, this vents the charging pipe 252, which thereby reduces the pressure in the piston chamber 85. Piston 84 then moves downwardly under action of spring 2' to seat the valve 248 and unseat valve 249. Seating of valve 248 closes the charging connection between the main reservoir I4 and emergency reservoir I3, while unseating of valve 249 connects the emergency reservoir to pipe and passage 93 leading to the fluid pressure operated device 32.

This device 32 then-rotates shaft I55 to its emergency position, to condition each of the brake systems for an application to a maximum degree. However, since in the embodiment of Fig. 4 there is no switch device to open the circuit to the suppression magnet valve section 2I9, this magnet valve will be energized to suppress the fluid pressure brakes while the dynamic and track brakes will be applied to a maximum degree. In this respect therefore the operation is different from that previously described for the embodiment of Fig. 1. The fluid pressure brakes will therefore not be applied until the dynamic brakes decrease in effectiveness near the end of the stop.

When the self-lapping portion 2l8 is actuated to emergency position, finger 234 engages stem 235 of the sanding valve 232, to also connect the emergency reservoir l3 to the sanding pipe H6, so as to cause sand to be deposited on the rails.

If the charging pipe 252 is maintained vented, the gradual escape or loss of fluid under pressure through choke I93 in the fluid pressure operated device 32 will ultimately permit shaft I55 to be returned to its release position, to thereby effect a release of the brakes.

In the embodiment of Fig. l the suppression magnet valve device is interposed between the main reservoir and the self-lapping portion of the control valve device. By this arrangement a smaller suppression magnet valve section may be employed, and fast applications and release of the brakes still obtained, because main reservoir pressure is available to force flow through the magnet valve device while the self-lapping portion has supply and release ports large enough to permit rapid supply to and release from the brake cylinder.

In the embodiment of Fig. 4, the suppression magnet Valve device is interposed between the self-lapping portion and the brake cylinder. When this is done it is necessary to employ the relay valve 238 in conjunction therewith in order to obtain the necessary flow capacity for fast applications and release. This location of the magnet valve device is desirable from the standpoint of avoiding any possible efiect on the operation of the self-lapping portion due to presence of the suppression magnet valve device in the supply line thereto.

While I have illustrated and described my invention with reference to one embodiment and one modification thereof, it is not my intention to be limited to the details of these or otherwise than by the spirit and scope of the appended claims herewith.

Having now described my invention, what 1' claim as new and desire to secure by Letters Patent, is:

1. In a vehicle brake system, in combination, fluid pressure brake means, dynamic brake means, magnetic track brake means, common control means for controlling applications of said three brake means, and fluid pressure means comprising a movable abutment subject on one side to pressure of fluid supplied to a chamber and on the other side to pressure of a spring, said abutment being connected to and being adapted to actuate said common control means upon supply of fluid under pressure to said chamber.

2. In a. vehicle brake system, in combination, a brake cylinder, a, magnetic track brake device, vehicle driving motors adapted to be connected to operate as dynamic brakes, a brake valve device operable to establish a communication through which fluid under pressure is supplied to said brake cylinder, control means for controlling the supply of current to said magnetic track brake device and for connecting said vehicle motors in a dynamic braking circuit, and means operated upon an increase in fluid pressure for operating said brake valve device and said control means.

3. In a vehicle brake system, in combination, fluid pressure brake means, dynamic brake means, magnetic track brake means, a brake valve device for establishing a communication through which fluid under pressure is supplied to effect an application of said fluid pressure brake means, electric control means for controlling applications of said dynamic and track brake means, common means for actuating said brake valve device and said electric control means, manually operated means adapted to be operated in effecting applications of said brake means for actuating said common means, and fluid pressure operated means operated upon a variation of fluid pressure therein for also actuating said common means.

4. In a vehicle brake system, in combination, fluid pressure brake means, electric brake means, means for establishing a communication through which fluid under pressure is supplied in effecting an application of said fluid pressure brake means, a first circuit in which current flows when application of said electric brake means. is efifected, electroresponsive means operable when energized to close said communication, a second circuit adapted when closed to supply current to said electroresponsive means, normally open contacts in said second circuit, and means responsive to current in said first circuit for closing said contacts.

5. Ina vehicle brake system, in combination, fluid pressure brake means, electric brake means, a circuit in which current flows when said electric brake means is applied, resistance in saidcircuit, electroresponsive means operable when energized to prevent so long as energized an application of said fluid pressure brake means, a source of current supply, and means controlled by the voltage drop across said resistance for controlling conergized to prevent an application of said fluid.

pressure brake means, switch means governed by the effectiveness of said electric brake means for supplying current to a circuit leading to said electroresponsive valve means, and a separate switch means operated upon a decrease in pressure for opening said circuit.

8. In a vehicle brake system, in combination, fluid pressure brake means, means operable to effect an application of said fluid pressure brake means, electroresponsive valve means operable when energized to prevent said application of said brake means, and means operated upon a decrease in pressure for preventing energization of said electroresponsive means.

9. In a vehicle brake system, in combination,

a brake cylinder, dynamic brake means, means for efiecting an application of each of said brake means, electroresponsive valve meansoperable to suppress the application of said fluid pressure brake means so long as said electric brake means is efiective above a chosen degree, and means operated upon a decrease in pressure for cutting said last means out of action to permit efiective application of said fluid pressure brake means.

10. In a vehicle brake system, in combination, a brake cylinder, electric brake means, a brake valve device operable to effect a supply of fluid under pressure to said brake cylinder, a magnet valve device disposed between said brake valve device and said brake cylinder and operable when energized to prevent supply of fluid under pressure to said brake cylinder by operation of said brake valve device, and switch means governed by the eifectiveness of said electric brake means for controlling energization of said magnet valve device, and operable when said effectiveness is above a chosen value to maintain said magnet valve device energized to a substantially constant degree, and when said effectiveness is below said chosen value to wholly deenergize said magnet valve device.

11. In a vehicle brake system, in combination, a brake cylinder, an electric brake device, a brake valve device operable to effect a supply of fluid under pressure from a reservoir to said brake cylinder, a magnet valve device disposed between said reservoir and said brake valve device and operable when energized to prevent supply of fluid. under pressure from said reservoir to said brake cylinder, and switch means governed by the effectiveness of said electric brake means for controlling energization of said magnet valve device, and operable when said effectiveness is above a chosen value to maintain said magnet valve device energized to a substantially constant degree, and when said effectiveness is below said chosen value to wholly deenergize said magnet valve device.

12. In a vehicle brake system, in combination, fluid pressure brake meanavehicle motors adapted to be operated as dynamic brakes, common control means for effecting a supply of fluid under pressure to said fluid pressure brake means and for disconnecting said motors from the source of power supply and reconnecting said motors in a dynamic braking circuit, manually operated means for actuating said common control means, and separate manually operated means for effecting an application of said fluid pressure brake means only independently of actuation of said first mentioned manually operated means, whereby power may be supplied to said vehicle driving motors while said fluid pressure brake means is applied.

13. In a vehicle brake system, in combination, electric brake means, fluid pressure brake means, common control means for controlling applications of said aforementioned brake means, fluid pressure operated means for actuating said common control means, means normally subject to fluid under pressure and operated upon a decrease in said pressure for supplying fluid under pressure to operate said fluid pressure operated means, and means for establishing at all times an unrestricted communication through which said fluid flows to said fluid pressure operated means.

14. In a vehicle brake system, in combination, fluid pressure brake means, magnetic track brake means, dynamic brake means, common control means for controlling applications of said three brake means, fluid pressure means operated upon supply of fluid under pressure thereto to actuate said common control means, a valve mechanism operated upon a decrease in pressure for supplying fluid under pressure to said fluid pressure means, and means establishing at all times an unrestricted communication through which said fluid flows to said fluid pressure operated means.

15. In a vehicle brake system, in combination, fluid pressure brake means, electric brake means, common control means for controlling applications of said two brake means, fluid pressure operated means operated upon a rapid supply of fluid under pressure thereto to actuate said common control means, a normally charged pipe, and a valve mechanism operated upon a decrease of pressure in said pipe for quickly efiecting a supply of fluid under pressure to said fluid pressure operated means through a communication which is at all times open.

16. In a vehicle brake system, in combination, a brake cylinder, a magnetic track brake device, vehicle driving motors adapted to be operated as dynamic brakes, a brake valve device operable to establish a communication through which fluid under pressure is supplied to effect a supply of fluid under pressure to said brake cylinder, a controller device adapted when operated to effect a supply of current to said magnetic track brake device and to connect said vehicle motors in a dynamic braking circuit, common means for operating said brake valve device and controller device, fluid pressure operated means operated upon supply of fluid under pressure thereto quickly for actuating said common means, a pipe normally charged with fluid under pressure, and means including a device operated upon a decrease of pressure in said pipe for effecting a supply of fluid under pressure to said fluid pressure operated means at a rapid and unrestricted rate.

17. In a vehicle brake system, in combination, electric brake means, fluid pressure brake means, two independent control means for controlling applications of said aforementioned 2W0 brake.

means, fluid pressure operated means operated upon a rapid supply of fluid under pressure thereto for actuating both of said control means to effect an application of the brakes, and safety control means for controlling the supply of fluid under pressure to said fluid pressure operated means, and operative to supply fluid under pressure thereto at an unrestricted rate.

18. In a vehicle brake system, in combination, a brake cylinder, a magnetic track brake device, vehicle driving motors adapted to be connected in a dynamic braking circuit, a brake valve device operable to establish a communication through which fluid under pressure is supplied to said brake cylinder, a controller mechanism operable to supply current to said magnetic track brake device and to connect said vehicle driving motors in a dynamic braking circuit, common means for actuating said brake valve device and controller mechanism, fluid pressure operated means operated upon a rapid supply of fluid under pressure thereto to actuate said common means, a pipe normally charged with fluid under pressure, means operated upon a decrease of pressure in said pipe for supplying fluid under pressure quickly and at an unrestricted rate to said fluid pressure operated means, and safety control means operated upon a decrease of pressure manually applied thereto for effecting a reduction of pressure in said pipe.

19. In a vehicle brake system, in combination, magnetic track brake means, dynamic brake means, a controller mechanism operable to an application position to effect an application of said two brake means, fluid pressure operated means operated upon a rapid supply of fluid under pressure thereto for actuating said controller device, and means for supplying fluid under pressure to said fluid pressure operated means at an unrestricted rate.

20. In a vehicle brake system, in combination, magnetic track brake means, dynamic brake means, a controller mechanism operable to an application position to effect an application of said two brake means, fluid pressure operated means operated upon a rapid supply of fluid under pressure thereto for actuating said controller device, a pipe normally charged, with fluid under pressure, and means operated upon a decrease of pressure in said pipe for effecting a supply of fluid under pressure to said fluid pressure operated means at an unrestricted rate.

21. In a vehicle brake system, in combination, vehicle driving motors adapted to be operated as dynamic brakes, control means adapted to be operated to disconnect said motors from a source of power supply and to connect said motor in a dynamic braking circuit, fluid pressure operated means for actuating said control means, a pipe normally charged with fluid under pressure, and means operated upon a reduction of pressure in said pipe for effecting a supply of fluid under pressure to said fluid pressure operated means at an unrestricted rate.

22. In a vehicle brake system, in combination, magnetic track brake means, dynamic brake means, a controller mechanism operable to application position to efiect an application of said two brake means, manually operated means for manually actuating said controller mechanism, and fluid pressure operated means for independently actuating said controller mechanism.

23. In a vehicle brake system, in combination, magnetic track brake means, dynamic brake means, a controller mechanism for controlling applications of said two brake means, a movable abutment subject on one side to pressure of fluid supplied to a chamber and on the other side to pressure of a spring, and being adapted upon a rapid supply or fluid under pressure to said chamber to actuate said controller device to application position, and means establishing a constant unrestricted communication between said chamber and the atmosphere.

24. In a vehicle brake system, in combination, a magnetic track brake device, vehicle driving mo-tors adapted to be operated as dynamic brakes, said motors having power supplied thereto from a trolley when operating as driving motors, a battery, and a control mechanism operable to application position to disconnect said driving motors from said trolley, to also connect said driving motors in a dynamic braking circuit, and to also connect said track brake device to said battery.

25. In a vehicle brake system, in combination, fluid pressure brake means, a pipe normally charged with fluid under pressure, a valve mechanism connected to said pipe and operative upon a decrease of pressure in said pipe for effecting a supply of fluid under pressure to said brake means, a valve device adapted to be located at the control station of the vehicle for varying the pressure in said pipe, said valve device being operable in a release position to open a communication through which fluid under pressure is supplied to said pipe, and a second valve device remote from said control station and also operable in a release position to open a communication through which fluid under pressure is supplied to said pipe, and operable in an application position to close said communication and to open a second communication through which fluid under pressure is released from said pipe.

26. In a vehicle brake system, in combination, electric brake means, fluid pressure brake means, a pipe normally charged with fluid under pressure, a valve mechanism connected to said pipe and operated upon a decrease of pressure in said pipe for effecting an application of said two brake means, a primary valve device normally under the control of an operator when in the regular control station of the vehicle for varying the pressure in said pipe, and operable when in a release position to effect charging of said pipe, and a second valve device remotely located from said control station and having two positions, one a position in which said pipe is open to a. source of fluid under pressure, and the other in which said communication is closed and said pipe is open to an atmospheric port.

JOSEPH C. MCCUNE. 

